Strapping apparatus

ABSTRACT

The present disclosure relates to a strapping apparatus of a strapping device for strapping packed goods with a strap. The strapping apparatus includes a strap-advancing apparatus for advancing the strap during the formation of a strap loop, a strap-retracting apparatus for retracting the strap after the strap loop has been formed to bring the strap in contact with the packaged goods, and a tensioning apparatus configured to increase a strap tension of the strap lying against the packed goods. The problem addressed by the present disclosure is improving said strapping apparatus to the effect that the strapping head can be made as compact as possible. This problem is solved in that only one common motor drives the rollers of the strap-advancing apparatus, the strap-retracting apparatus, and the tensioning apparatus.

This application is a national stage entry of PCT/CH2015/000014, filed on Feb. 10, 2015, which claims priority to and the benefit of Switzerland Patent Application Nos.: (1) 183/14, filed on Feb. 10, 2014; (2) 182/14, filed on Feb. 10, 2014; and (3) 181/14, filed on Feb. 10, 2014, the entire contents of each of which are incorporated herein by reference.

The present disclosure relates to a strapping device of a strapping apparatus for strapping packaged articles with a strapping band, in particular with a plastics strapping band, which strapping device a band advancement device for the advancement of the strapping band during the formation of a band loop, having a band retraction device for the retraction of the strapping band after the formation of the band loop for the purposes of causing the strapping band to be laid against the packaged article, and having a tensioning device by way of which a band tension in the strapping band laid against the packaged article can be increased.

Strapping apparatuses of said type, like those to which the present disclosure also relates, may be formed as a static installation which is utilized for equipping relatively large packaged articles, or multiple individual packaged articles placed together to form a packaged article unit, with one or more band straps. The band straps are normally formed from a band which is drawn from a supply roll and laid as a ring-shaped strap around the packaged article. For this purpose, the strapping band is shot with its free end first into a channel of the strapping apparatus, which channel surrounds the packaged article, with a spacing, in the manner of a portal or in ring-shaped fashion. Normally, as soon as the band end has reached a particular point in the channel, the band end is clamped and the band is then retracted again. As a result, the loop of the strapping band is tightened and the band passes out of the channel and into contact with the packaged article. Subsequently, the band is pulled taut and, in the process, a band tension is applied to the band, and the band ring or the band loop is equipped with a fastening and is cut off from the supply roll. As strapping band, use is made both of metallic bands and of plastics bands. The strapping apparatuses are normally adapted to the strapping band types used therewith, in particular with regard to the connecting device by way of which two band layers, which lie one over the other in sections, of the strapping bands can be non-detachably connected to one another.

In the case of previously known solutions, the strapping apparatus generally has multiple rollers of the band advancement device, of the band retraction device and of the tensioning device, which rollers are motor-driven for the purposes of realizing, by way of contact between the circumferential surfaces of the respectively driven rollers with the strapping band, the respectively desired band movement, specifically the band advancement, a band retraction or a pulling-taut action by way of the tensioning wheel. These three functional components, that is to say band advancement device, band retraction device and tensioning device, normally require a multiplicity of components to impart the individual movements to the band in a functionally reliable manner. As a result of this, the strapping device, which is normally in the form of a strapping head, is of relatively large construction, and requires a large volume in the strapping apparatus. Furthermore, this results in a high weight of the strapping device.

The present disclosure is therefore based on the object of improving a strapping apparatus for strapping packaged articles with a strapping band such that the strapping head can be designed to be as compact as possible.

Said object is achieved, in the case of a strapping device of the type mentioned in the introduction, by only one motor for driving the rollers which are driven in rotation by motor action in the band advancement device, in the band retraction device and in the tensioning device. Owing to the fact that the number of motors directly provided for the generation of the band movements is reduced to just one motor, not only is it possible for the strapping device according to the present disclosure to be realized in a more compact form, but it is also possible in this way to achieve an increase in functional reliability and a reduction in the maintenance requirements of strapping devices according to the present disclosure, which are normally in the form of strapping heads of static strapping apparatuses. In the context of the present present disclosure, a “motor” may be understood to mean any drive by way of which a band movement, including minimal band displacement lengths, can be realized for the purposes of generating an increased band tension. Such motors are often in the form of electric motors, though it is also possible for pneumatic, hydraulic or other drives to be provided in conjunction with the present disclosure.

In an expedient refinement according to the present disclosure, it may be provided that, by way of the only one motor, in each case one roller of the tensioning device, one roller of the band advancement device and one roller of the band retraction device can be driven. Therefore, all three functional units should be rigidly (in the sense of non-detachably) operatively connected or operatively connectable to the one drive motor. The latter may be realized for example by way of one or more freewheels or couplings by way of which the respective operative connection to one or to several of the functional units can be temporarily eliminated and restored as required. In one embodiment, it is however also possible for no switchable couplings or freewheels to be provided, whereby

A further embodiment of the present disclosure—which may also be of independent significance independently of the number of wheels, rollers and motors used for the imparting of movements to the band and independently of the design of the tensioning wheel—may provide an actuable means by which at least one wheel of a wheel pair of the advancing device can be switched into a state in which the strapping band can be displaced between the wheel pair in a direction opposite to the band advancement movement, without a corresponding motor drive movement being transmitted to the strapping band. With the present disclosure, provision is thus made for the state of the wheel pair to be changed from a state in which the band is clamped between said wheels, which state permits in particular the advancement of the band, into a state in which the band can move through between the wheel pair regardless of a driven movement of a wheel of the wheel pair. According to the present disclosure, the clamping state between the wheel pair, which clamping state is provided for the transmission of a motor drive movement via one of the two wheels to the strapping band, is reduced at least to such an extent that slippage or an increased gap can form between the band and the wheel pair. If an enlarged gap between the circumferential surfaces of the wheels is generated in the event of the clamping action being eliminated, said gap should be larger than the band thickness. The clamping action may for example be reduced simply by virtue of a pressure force with which the two wheels are pressed against one another being reduced, for example by way of a variably adjustable magnitude of said pressure force. Such a reduction of the clamping action may alone be sufficient for a strapping band to be able to move between the wheel pairs of its own accord.

The possibility of movement of the strapping band between the wheels of the wheel pair may however alternatively also be realized by virtue of an operative connection between a driven wheel and its drive being eliminated, such that both wheels of the wheel pair are rotatable freely and without a holding torque of the drive device. Such an elimination of an operative connection may be performed for example by way of a switchable clutch in the drive train of the driven wheel. By way of said switchable clutch, it is also possible for the operative connection to be restored in order for a drive movement, in particular a band retraction movement, to subsequently be imparted by the driven roller to the strapping band again.

By way of free rotatability of the wheel pair, or at least slippage or an adequately large gap between the wheels, it is made possible for the strapping band, immediately after or even during the generation of the band loop, to discharge excess band length of the band loop through between the wheel pair, whereby it is sought to as far as possible prevent the formation of a convolution. An incipient excess band length in the strapping channel leads to buckling in the band loop and thus to compressive and/or bending stresses in the strapping band. Normal strapping bands exhibit a flexural rigidity which has the effect that such bands have the tendency to dissipate compressive and bending stresses by seeking to assume planar and rectilinearly running orientation. This is advantageously utilized by the present disclosure in that, through the creation of a possibility for movement of the band through between the wheel pair, excess band length can move in particular of its own accord out of the band channel again between the wheels owing to the self-relaxation of the band.

In a refinement of said further aspect of the present disclosure, a strapping device in the case of which an advancing movement of the band through the strapping device is provided for the formation of a band loop and, here, the band is clamped between a motor-driven roller and a counterpart roller, a clearance device can be provided. According to this aspect of the present disclosure, in the case of a strapping device, the clearance device may be provided for performing a clearance-generating process between the driven roller and its counterpart roller, by way of which a spacing between the driven roller and its counterpart roller is generated or enlarged and is subsequently reduced in size again. In this context, therefore, the expression “generating a clearance” may be understood to mean the generation of a spacing.

With this measure according to said further aspect of the present disclosure, it is possible for the formation of a convolution in the band noose or loop, in particular in the region of a band drive device of the strapping device, such as has hitherto often arisen after the completion of the band advancement process in the case of a high band advancement speed and can lead to malfunctions of the strapping device, to be at least substantially avoided. Excess band can move in the direction of the band store again of its own accord through the gap, enlarged owing to the clearance-generating process, between the two rollers. Such a backward movement of a band section through the enlarged gap between the two rollers may take place automatically, in particular owing to the impetus or the kinetic energy present in the band owing to the band advancement that has previously taken place and the flexural rigidity of the band, without the need for a corresponding motor-generated drive movement to be imparted to the band in the same direction.

It is advantageously possible for the clearance-generating process between the two rollers to be eliminated again before the band retraction process effected by motor drive movement, and for the two rollers to be placed in contact with one another again. The clearance-generating process is thus performed at a time between the band advancement process and the band retraction process. A time overlap between the band advancement process and/or the band retraction process, on the one hand, and the clearance-generating process, on the other hand, is possible here but is not imperative.

In a further expedient embodiment of the present disclosure according to this aspect, the non-motor-driven counterpart roller may be arranged on a rotatable eccentric. Here, the clearance-generating device may act on the eccentric in order, by way of rotation of the eccentric and the eccentricity, to generate between the two rollers a gap which is greater than the band thickness. After the completion of the clearance-generating process, the eccentric can be rotated in the then opposite direction again, whereby the two rollers clamp the band between them again and a band retraction process can be performed by way of the two rollers. Said embodiment of the present disclosure has inter alia the advantage that a fast movement of the counterpart roller for the generation of a spacing to the driven roller, and an advancing movement toward the driven roller again, are possible by way of an eccentric with a relatively small structural space requirement. In other embodiments of the present disclosure, the spacing between the two rollers for the clearance-generating process may self-evidently also be realized in some other way, for example by way of a pivoting movement or a linear movement of at least one of the two rollers.

In a further expedient embodiment of the present disclosure, it may be provided that the clearance-generating movement is realized by way of a linearly movable driven element such as for example a stroke-performing piston. Such stroke-performing elements are available in a variety of forms and with different drive principles. With such stroke-performing elements, it is possible the drive movement to form particularly functionally reliable clearance-generating devices. Furthermore, with such drive elements, it is also possible with relatively little outlay for existing strapping apparatuses to be retrofitted with a clearance-generating device.

Further embodiments of the present disclosure will emerge from the claims, from the description and from the drawing. The content of disclosure of the patent claims is hereby incorporated by reference into the description. The present disclosure will be discussed in more detail below on the basis of exemplary embodiments which are illustrated purely schematically in the figures, in which:

The present disclosure will be discussed in more detail on the basis of exemplary embodiments which are illustrated purely schematically in the figures.

FIG. 1 is a highly schematized illustration of a strapping apparatus according to the present disclosure which is equipped with a strapping head according to the present disclosure.

FIG. 2 is a perspective illustration of a strapping head according to the present disclosure.

FIG. 3 is a perspective illustration from above of the strapping head from FIG. 2 integrated into a band guide of a strapping apparatus.

FIG. 4 shows a side view of the strapping head from FIG. 2, in the case of which a component is situated in a pivoted-out servicing position.

FIG. 5 is a perspective partial illustration of the strapping head from FIG. 2, with the band drive device being illustrated.

FIG. 6 shows a front view of the band drive device from FIG. 5.

FIG. 7 is a perspective illustration of a tensioning wheel according to the present disclosure with a partial illustration of the knurling of the circumferential surface of the tensioning wheel.

FIG. 8 shows a front view of the tensioning wheel from FIG. 7.

FIG. 9 is a cross-sectional illustration of the tensioning wheel along a diameter line.

FIG. 10 shows a component of a lever mechanism for a counterpart roller of the band drive device.

FIG. 11 shows a further component of the lever mechanism of the counterpart roller in a perspective illustration.

FIG. 12 shows the component from FIG. 11 in a front view.

FIG. 13 is a sectional illustration of the component from FIGS. 11 and 12.

FIG. 14 is an exploded illustration of a further exemplary embodiment of a tensioning wheel.

FIG. 15 is a perspective illustration of the tensioning wheel from FIG. 14.

FIG. 16 shows a front view of the tensioning wheel from FIGS. 14 and 15.

FIG. 17 is a sectional illustration of the tensioning wheel from FIGS. 14-16.

FIG. 18 shows a further exemplary embodiment of a band drive device according to the present disclosure with a clearance-generating device in a partial illustration of a strapping head.

FIG. 19 shows the band drive device from FIG. 18 in an illustration in which a clearance has been generated between a counterpart roller and the driven roller that interacts therewith.

FIG. 1 shows a strapping apparatus 1 which is equipped with a controller 2, a supply device 3 for storing and making available a strapping band, and with a strapping head 5. The strapping head 5 serves inter alia for the generation of an advancement movement and for the generation of a retraction movement of the strapping band. Said strapping head is furthermore equipped with a tensioning device, for imparting a band tension to a band loop, and a fastening device for generating a fastening on the strapping band. Furthermore, the strapping apparatus has a band guide 6 by way of which the band can be mechanically and automatically laid around a packaged item 7 on a predefined path. A welding and clamping unit 16 is also integrated into the strapping head 5. Aside from the strapping head 5, these are components that are known per se of strapping apparatuses.

The strapping head 5, which is arranged together with the band guide 6 on a frame 8 and which is separately illustrated in FIG. 2 has a band drive device 15. Band drive devices are basically already known, for which reason substantially the differences in relation to previously known band drive devices will be discussed below. The band drive device according to this exemplary embodiment may be equipped in particular with one or more roller pairs and possibly with further individual diverting rollers. The latter however do not participate in the generation of the band movement and are provided only for determining the band running direction. Of the three rollers 11, 12, 13 in the exemplary embodiment which generate the band movements, at least one of the rollers 11, 12, 13 should be motor-driven for the purposes of generating a band advancement or band retraction movement. Here, in each case one roller 11, 12, 13 of the roller pairs formed from said rollers, between which roller pairs the strapping band is led through and in the process an advancement, retraction or tensioning movement, and possibly a tension-relieving movement, is transmitted to the band, should be driven.

The strapping head 5 has two components: a control component 16 and a band handling component 17. In the exemplary embodiment, the control component 16, aside from the execution of control functions for the components of the strapping device, has further functions, for example the generation of fastenings between the two belt layers of a strap and the cutting of the strapping band from the band supply. The control component 16 is in this case mounted on a partial carrier 18 of the strapping head, wherein the partial carrier 18 is in turn detachably fastened to a common main carrier 19 of the strapping head 5. As can be seen in particular from FIG. 4, the partial carrier 18 of the control component 16 is pivotable about an axis 23. The elements of the band handling component 17 are fastened, without a dedicated partial carrier, directly to the main carrier 19 of the strapping head. In the exemplary embodiment, the control component 16 is provided substantially for performing control and coordination functions out of the functions performed by the strapping head. The band handling component 17 and the components attached thereto are, by contrast, provided for acting directly on the strapping band.

A band advancement device 20, a band retraction device 21 and a tensioning device 22 are integrated into the band handling component 17 of the strapping head 5. In the exemplary embodiment shown here, common rollers 11, 12; 13 are provided for the band advancement, band retraction and tensioning devices 20, 21, 22. Of the total of only three rollers 11, 12, 13, two rollers 11, 12 are motor-driven rollers. The two rollers 11, 12 are driven by the same (only one) motor 14, in the exemplary embodiment an electric motor. For this purpose, it may for example be provided that, from the common motor 14, in each case one drive train leads to one of the two rollers 11, 12. Here, the roller 11 is provided both as a drive wheel for the band advancement (band advancement wheel) and as a drive wheel for the band retraction (band retraction wheel). In order that, in the exemplary embodiment illustrated, said two functions can be performed by way of only one wheel, the roller 11 can be driven in both directions of rotation by the same drive motor 14. Here, in the illustration of FIG. 6, the direction of rotation counterclockwise is the band advancement direction, and the direction of rotation clockwise is the band retraction direction. As shown in FIG. 2, the motor drive movement is transmitted to both wheels or rollers 11, 12 by the common motor 14 by way of a mechanism device. In the present exemplary embodiment, the mechanism device 14 a comprises a toothed-belt mechanism which transmits the drive movement from the motor shaft to a further shaft running parallel to the motor shaft. On said further shaft there are arranged two gearwheels which belong in each case to a further one of two partial mechanisms of the mechanism device. One of said two partial mechanisms of the mechanism device transmits the motor drive movement to the roller or the wheel 11, and the other partial mechanism transmits the motor drive movement to the tensioning wheel 12. Depending on the direction of rotation of the motor shaft, it is thus the case in the exemplary embodiment that both the tensioning wheel 12 and the wheel 11 rotate in different directions of rotation.

In the installed position of the strapping head depicted in FIGS. 5 and 6, the roller 11 is arranged above the roller 12. The roller 12 is a constituent part of the tensioning device 22 and has the function of the tensioning wheel. Said roller has a considerably greater diameter than the roller 11. The tensioning wheel 12, owing to the rigid connection to the motor 14 and the drive movements in both directions of rotation performed by the motor, can likewise be driven in both directions of rotation. For the imparting of the intended band tension to the strapping band, in particular to the band loop, the tensioning wheel however utilizes only the drive movement in the tensioning direction, that is to say the clockwise direction of rotation as viewed in the illustration of FIG. 6. In certain embodiments, a release of tension from the band section which is situated in the strapping head, and which is no longer part of the band loop, may be realized by way of a rotational movement of the tensioning wheel, taking place after the tensioning process, in the direction of rotation opposite to that during the tensioning process. The drive movements both for the tensioning movement and for the tension-relieving movement originate from the same drive motor as for the roller 11. As an alternative to the exemplary embodiment of the present disclosure illustrated here, it is possible in other embodiments for a switchable clutch to be provided in the drivetrain (not illustrated in any more detail) from the motor to the two rollers 11, 12, by way of which clutch the drive movement can be conducted either to the roller 11 or to the roller 12. Aside from embodiments in which the tensioning wheel is in turn capable of being driven in both directions of rotation, it may also be provided that the tensioning wheel can also be driven only in the direction of rotation provided for the tensioning process.

As can be seen from the illustration of FIG. 6, the roller 13 is adjacent both to the roller 11 and to the tensioning wheel 12. The roller 13 is not driven in rotation and is pivotably articulated by way of a pivoting device. The pivoting device is operatively connected to a drive by way of which the roller can perform (motor-) driven pivoting movements. By way of the pivoting movement, the roller 13 which functions as counterpart roller can be placed either in contact with the roller 11 or in contact with the tensioning wheel 12, wherein, in the respective end position of the pivotable roller 13, the strapping band is situated in each case between one of the rollers 11, 12 and the roller 13. Depending on which of the rollers 11, 12 the counterpart roller 13 bears against, the counterpart roller 13 then forces the band against the corresponding roller 11, 12 such that the corresponding roller 11, 12 can transmit its rotational movement with the least possible slippage as an advancement, retraction or tensioning movement, and possibly as a tension-relieving movement, to the strapping band. The counterpart roller 13 is thus, together with the roller 11, both a constituent part of the band advancement device and a constituent part of the band retraction device. Together with the tensioning wheel 12, the counterpart roller 13 is also a constituent part of the tensioning device 22. By way of this configuration according to the present disclosure, it is possible for the fourth roller that has hitherto been conventional in previously known solutions to be dispensed with. In the case of said previously known solutions, the drive roller and the tensioning wheel are in each case fixedly assigned one of two counterpart rollers. The 3-roller solution according to the present disclosure can permit a considerably more compact embodiment in relation thereto.

The rollers 11, 12, 13 are, in the strapping head 5, furthermore a constituent part of a band guide channel 28 which predefines the profile and the advancement and retraction path of the band. The band guide channel 28 is in turn part of the band guide 6. As can be seen in FIG. 6, the strapping head 5 has a first interface 29 at which the strapping head 5 adjoins the supply roll side of the band guide. That end of the band guide channel 28 which is formed here is in the form of a quick-change interface. This has a channel piece 31 which can be clamped to the strapping head by way of a pivotable clamping lever 30 and through which the band is supplied into the strapping head. The channel piece 31 ends directly in front of the circumferential surface 11 a of the roller 11, such that the strapping band can be supplied at least approximately tangentially to the circumferential surface 11 a of the roller 11. If the roller 13 is situated in its end position in which it is pivoted toward the roller 11, the band is led through between the rollers 11, 13, wherein the roller 13 forces the band against the roller 11.

As viewed in the band advancement direction 32, the band passes, in its further progression, to the tensioning wheel 12. Here, proceeding from the counterpart roller 13, a circular-arc-shaped channel section 28 a which extends over approximately 180° of the circumference of the tensioning wheel 12 is formed by way of suitable channel-forming means. With regard to the band thickness, the channel section 28 a is formed so as to be considerably wider than the band thickness. The inner delimitation of the channel section is formed by that section of the circumferential surface 12 a of the tensioning wheel 12 which is situated in each case in the region of the channel section. The outer delimitation of the channel section 28 a as viewed radially has guide plates and an outer channel segment which is pivotable together with the counterpart roller 13, by way of which outer channel segment the outer channel section can be kept closed despite the pivotable counterpart roller 13 being situated in the region of the outer channel section. Without the pivotable channel segment 33 or some other element of similar action, there would possibly be an open point of the channel section at least in one of the two pivoting end positions of the counterpart roller 13, which open point could possibly have an adverse effect with regard to reliable band guidance.

FIGS. 7, 8 and 9 show the tensioning wheel in three illustrations. Said tensioning wheel has a ring 37 which is equipped with a recess 38 which is provided for the connection of the tensioning wheel 12 to a shaft of the drive, in particular to a shaft of a mechanism of the drive. FIG. 2 shows the tensioning wheel 12 mounted on the shaft. As can likewise be seen from FIG. 6, the circular tensioning wheel has a circumferential surface 12 a with an at least substantially constant width. The tensioning wheel 12 is equipped, on its circumferential surface 12 a, with a knurling or toothing 39 by way of which the engagement conditions of the tensioning wheel 12 on the strapping band are improved. Instead of a knurling or toothing 39, it would also be possible for any other geometrically defined or undefined roughening of the circumferential surface 12 a of the tensioning wheel to be provided, by way of which possible slippage between the tensioning wheel and the strapping band during the tensioning process can be at least substantially prevented.

A groove 40 with a relatively small width is formed over the entire circumference of the circumferential surface 12 a at least approximately centrally—in relation to the width of the tensioning wheel 12—and so as to be spaced apart from the lateral edges of the tensioning wheel, which groove is formed so as to be considerably deeper than it is wide. In the exemplary embodiment, two resiliently elastic O-rings 43, 44 are situated one above the other in the groove 40, said O-rings being arranged radially one behind the other in the groove 40. Here, one of the O-rings 43 is arranged with a relatively small spacing to the axis of rotation of the tensioning wheel 12, and the other O-ring 44 is arranged with a relatively large spacing to the axis of rotation of the tensioning wheel 12. The width of the O-rings 43, 44 is in this case provided so as to approximately correspond to the width of the groove 40. The two O-rings 43, 44 are situated entirely within the groove 40. The two O-rings 43, 44 are formed from resiliently elastic material.

On the outer of the two O-rings 43, 44 there is seated a ring 45 which is provided as a spacer element and which, in the exemplary embodiment, is formed from a metallic material. In this exemplary embodiment, the ring 45 is elastically deformable. It would likewise be possible for the ring to be of substantially rigid or dimensionally stable form. To realize said elastic characteristics of the ring, it would also be possible for the ring 45 to be formed from one or more materials other than a metallic material, for example from an elastic plastic. In the exemplary embodiment, said metal ring 45 is, in terms of its cross section, provided so as to have a width B smaller than its height H. The height of the O-ring is, with regard to the groove depth and the height of the O-rings, configured such that the ring projects with a height H₁ out of the groove 40. Thus, in its unloaded state shown in FIG. 9, the ring 45 projects beyond the circumferential surface 12 a of the tensioning ring 12, in particular over its entire circumference or over the entire circumference of the tensioning ring 12.

At the start of the strapping process, the strapping band is pushed at high speed, with its free band end first, from the strapping head 5 through the band guide 6. For this purpose, the counterpart roller 13 is in contact with one side of the band. The band is forced with its other side against the motor-driven roller 11 by the counterpart roller. The rotational drive movement of the roller 11 in the advancement direction is in this way transmitted to the strapping band, which effects the advancement movement thereof in the advancement direction. Downstream of the region in which the band emerges from the gap between roller 11 and counterpart roller 13, the band comes into contact with the tensioning wheel 12, but without exerting a significant pressure on the tensioning wheel 12.

After the band has been pushed all the way through the band guide 6, the band end reaches the closure head again. Here, the band end actuates a limit switch, whereby the advancement movement is stopped and the band end is clamped. These and other activation and deactivation processes of components of the closure head are performed by the control component 16 which, for this purpose, is equipped with a motor-driven camshaft control arrangement such as is basically known.

The camshaft control arrangement of the control component 16 now sets the roller 11 in motion in a direction of rotation reversed in relation to the advancement direction. The strapping band, which remains clamped between the roller 11 and the counterpart roller 13, is hereby moved in the reverse direction, that is to say in the band retraction direction 48. The circumferential length of the band loop, the band end of which remains clamped, is hereby continuously shortened. The band is hereby pulled out of the band guide 6 and, as a result, laid around the respective packaged item.

FIG. 6 illustrates the tensioning wheel 12 during the band retraction process. As can be seen from said illustration, it is the case during the band retraction process that the band comes into contact with the tensioning wheel 12. The strapping band bears against the tensioning wheel 12 substantially over the entire circular-arc-shaped channel section 28 a, similarly to the situation also encountered during the subsequent tensioning process. The band is duly retracted here, but, owing to its ability to yield to said movement by moving, as intended, out of the band guide, it is nevertheless the case during said phase that only a relatively low band tension is applied to the band of the band loop. As a result of said contact with the tensioning wheel 12 and of the ring 45 which projects in relation to the circumferential surface, the band bears not against the circumferential surface of the tensioning wheel 12 but against the ring 45 situated in the circumferential surface 12 a. Said contact with the spacer element, which, in the exemplary embodiment, is in this case in the form of a ring 45, has the effect that, during the band retraction, the band cannot be damaged by the knurling or toothing 39 of the circumferential surface 12 a.

After the band has been laid against the packaged article as a result of the band retraction, the controller switches from band retraction to generation of a band tension, whereby it is the intention for the band laid against the packaged article to be pulled taut. For this purpose, it is firstly the case that the counterpart roller 13 is pivoted from its position of contact against the roller 11 into a position of contact against the tensioning wheel 12. The tensioning wheel 12, which is rotated in the same direction of rotation as the roller 11 was previously, rotates at a lower rotational speed but with a greater torque, and pulls further on the strapping band. Owing to the absence of pressure of the counterpart roller 13, it is by contrast now the case that the band no longer bears against the roller 11, which continues to be driven in the exemplary embodiment and which rotates at a higher speed, in such a way that the roller 11 could transmit its movement to the band. Since, at this stage, the strapping band already bears against the packaged article, the band is, by the tensioning wheel 12, retracted at most over a short length in relation to the band retraction phase. During said tensioning phase, it is in particular the case that a relatively high band tension is applied to the band.

Already at the start of the tensioning phase, the pressure of the counterpart roller 13 in the direction of the tensioning wheel and the band situated in between causes the ring 45 to be forced in the direction of the groove base and thus also in the direction of the axis of rotation of the tensioning wheel 12 as viewed in a substantially radial direction. In this way, it is the case already at the start of the tensioning phase that the band bears against the ring 45 and forces the latter likewise, at least in the region of the counterpart roller 13, in the direction of the groove base. Thus, already at the start of the tensioning process, the ring 45 has, in the region of the counterpart roller 13, a smaller spacing to the axis of rotation of the tensioning wheel than in its unloaded state, for example during the band advancement or the band retraction phase.

The torque transmitted from the tensioning wheel 12 to the band during the further course of the tensioning process, which torque is higher than that in the band retraction phase of the roller 11, results in a greater reaction force of the band. Said greater reaction force now has the effect that the band forces the ring 45 into the groove not only in the contact region with the counterpart roller 13 but over its contact length (wrap angle as viewed in the circumferential direction) with the ring 45, whereby the band now bears, along its wrap angle on the tensioning wheel 12, against the circumferential surface of said tensioning wheel. Along its wrap angle on the tensioning wheel, the band forces the ring into the groove counter to the spring forces of the O-rings. Depending on the characteristics of the ring 45, said ring is deformed possibly elastically as a result, and, along that circumferential section in which the strapping band does not bear against the tensioning wheel, said ring can partially (with regard to its height) emerge from the groove again. Outside the wrap angle of the band on the tensioning wheel, the ring 45 may in this case project out of the circumferential surface to a greater extent than in the unloaded state, in the case of which it projects with a height H₁. Since the ring is arranged rotationally conjointly in the groove, it is the case, in a manner dependent on the respective rotational position of the tensioning wheel 12, that each individual point of the ring is forced into the groove 40, and emerges from said groove again, in alternating fashion until, owing to the rotation of the tensioning wheel, said point arrives again at the point at which the band wraps around a section of the circumferential surface and thereby forces the ring into the groove along said section. It is thus possible, despite the means provided for preventing the strapping band from coming into contact with the circumferential surface of the tensioning wheel during the band retraction phase, for functionally reliable contact of the band with the same tensioning wheel to nevertheless be achieved during the band tensioning phase.

The counterpart roller 13 can advantageously be forced with different pressing forces firstly against the roller 11 (advancement roller or retraction roller) and secondly against the tensioning wheel 12 (during the use of the strapping device in each case with a strapping band situated in between). Higher pressing forces against the tensioning wheel than the possible pressing forces against the roller 11 can be advantageous for high functional reliability and for the possibility of applying high band tensions to the strapping band. Therefore, below, it will be discussed how, in one embodiment of the present disclosure, despite the pivoting movement of the counterpart roller 13 between two end positions, different pressing forces can be realized in the end position.

For this purpose, the counterpart roller 13 is arranged on an eccentric 50 which, in turn, is arranged on a shaft 51 of a carrier 52. The carrier has, spaced apart from the shaft 52, a receptacle 53 which is provided for arrangement on the bearing point 54 of the roller 11 (FIGS. 5 and 6). Here, the receptacle 53 is freely rotatable about its axis of rotation on the bearing point 54 of the roller 11 and can thus perform pivoting movements about its axis of rotation.

In the region of the counterpart roller 13 and of the roller 11, there is provided a parallelogram which has multiple levers 57, 58, 59 which are pivotably articulated on one another. The parallelogram 56 has a long vertical lever 57, a horizontal lever 58 and a short vertical lever 59. The parallelogram is pivotably articulated on the long vertical lever 57 and on the short vertical lever 59. The levers 57 and 59 have pivot bearing points 60, 61 for this purpose. Via a bell-shaped curve 62, it is possible for a rotational movement to be transmitted to the long vertical lever 57, which rotational movement leads to the pivoting movement of the lever 57 about its pivot bearing point 60. In the illustration of FIG. 12, the pivoting movement of the lever 57 takes place clockwise.

In this way, at the articulation point of the short vertical lever, the lever 58 also pulls said short vertical lever in the direction of the lever 57, whereby the vertical lever 59 is, in the illustration of FIGS. 11 and 12, likewise pivoted clockwise about its pivot bearing point 62. As a result, an oblique surface 64 formed on the short vertical lever 59 pushes against a bearing 51 arranged on the shaft 51. As a result, the oblique surface performs a movement clockwise (in the illustration of FIG. 12) and has the tendency to assume a horizontal orientation. As a result, the carrier 52 performs a pivoting movement, whereby the counterpart roller 13 is pivoted from its end position against the roller 11 in the direction of the tensioning wheel 12.

When it reaches the tensioning wheel, the counterpart roller bears against the tensioning wheel and can perform no further pivoting movement. The lever 57 however pivots further, whereby the bearing point 65 of the eccentric 50 is moved counterclockwise in the direction of an L-shaped carrier 66. After the bearing point 65 pushes against the L-shaped carrier 65, the movement of the bearing point 65 stops, and said bearing point is situated at least approximately in a line with an upper bearing point 66, the axis of rotation 67 of the counterpart roller 13 and the axis of rotation 68 of the tensioning wheel 12. A spring element that has hitherto generated the pressing force of the counterpart roller 13 is, as a result, no longer active.

A further movement of the lever 57 during its pivoting movement now has the effect that the lever 59 can also perform no further movement, and therefore two parts 58 a and 58 b of the horizontal lever 58 are pulled apart. A spring element 70 arranged between the two parts 58 a, 58 b of the lever is hereby compressed, whereby the spring force thereof increases. This leads to a torque of the lever 59 about the pivot bearing point 61 with the lever arm of the spacing of the pivot bearing point 61 from the articulation point 71 of the lever 58 on the lever 59. As a result, the oblique surface 64 pushes, in the form of a torque about the pivot bearing point 61, against the bearing, which now leads to a pressing force of the roller 13 against the tensioning wheel. By way of a correspondingly dimensioned and designed spring element 70 and corresponding lever ratios, it is possible in this way to realize high pressing forces of the roller 13 against the tensioning wheel.

A restoration of the parallelogram can be realized by way of a further spring 73 arranged on the peg 72 of the lever 5.

Alternative embodiments of components and assemblies discussed above will be described below. Here, substantially only differences in relation to the corresponding components from FIGS. 1 to 13 will be discussed. Where said embodiments include identical or similar configurations to those in the exemplary embodiment of FIGS. 1 to 13, these will not be discussed in any more detail below; the content of disclosure of the exemplary embodiments of FIGS. 1 to 13 is however also incorporated by reference for the exemplary embodiments of FIGS. 14 to 19.

FIGS. 14, 15, 16 and 17 illustrate a further embodiment of a tensioning wheel 112 according to the present disclosure. The tensioning wheel 112 may be divided longitudinally in terms of its width, approximately in the center, wherein the two parts 112 b, 112 c of the tensioning wheel 112 are detachably connectable to one another by way of suitable fastening elements, for example screws 114. In the region of said parting plane, which need not run in a flat manner, an encircling groove 140 is formed in the outer ring 137 of the tensioning wheel 112, which groove is open toward the circumferential surface 112 a of the tensioning wheel 112 and is narrowed or decreased in size toward said circumferential surface.

One or more restoring elements may be arranged in the groove 140. In the exemplary embodiment, as a restoring element, there are arranged elastic ring sections 143, for example multiple resiliently elastic O-ring sections 143. Said ring sections are distributed in the groove 140 at regular intervals with respect to one another, as is the case in the exemplary embodiment with a total of four ring sections 143. The restoring elements 143 are situated below one or more spacer elements. In the exemplary embodiment, only one spacer element 145, in the form of a closed ring, is provided. An outer diameter of the ring 145 arranged in the groove is in this case dimensioned such that, in the unloaded state of the ring 145, said ring projects with its outer circumferential surface beyond the circumferential surface 112 a of the tensioning ring 112. The ring 145 is situated with its inner circumferential surface in the groove. The restoring elements are attached to the inner circumferential surface of the circular and substantially dimensionally stable ring 145. In other embodiments, it is also possible for a different number of spacer elements, and a different number of restoring elements, to be provided.

As a result of contact of the strapping band against the ring 145, and as a result of a certain minimum pressure force being exerted on the ring along a certain angle range along a section of the circumference of the tensioning wheel by the strapping band, it is possible for approximately that section of the ring 145 which projects beyond the groove along said angle range to be forced into the groove 140, such that, in said positionally static angle range of the tensioning wheel 112, the strapping band comes into contact with the circumferential surface 112 a of the tensioning wheel 112 and can be driven along by the circumferential surface 112 a during the movement of the tensioning wheel 112. The ring 145, which substantially cannot be deformed by the expected forces acting thereon in the exemplary embodiment, and which is thus dimensionally stable, is thus arranged slightly eccentrically in relation to the axis of rotation of the tensioning wheel during said process. The ring 145 hereby projects, with its section not encompassed by the wrap angle of the band, out of the groove 140 further than when the tensioning wheel is in the state in which it is not subject to load by the strapping band. As a result of the ring 145 being relieved of the load of the strapping band, or when a pressure force exerted on the ring 145 by the strapping band is not sufficient, it is possible, after the completion of the tensioning process, for the elastic restoring forces of one or more of the ring sections 143 to cause the ring 145 to project out of the groove again over its entire circumference.

By way of this arrangement, it is possible, during the tensioning process, during which the tensioning band exerts an adequately high pressure force on the ring 145 situated in the wrap region of the strapping band, for the ring 145 to be forced in sections into the groove 140. During the retraction process, during which only a relatively low tensile stress is present in the strapping band, the pressure force on that section of the ring 145 which is presently arranged in the wrap region of the band is not high enough to force said ring section entirely into the groove 140. As a result, the band bears against the section of the ring 145 and not against the surface of the tensioning wheel 112. The ring 145 holds the strapping band so as to be spaced apart from the circumferential surface of the tensioning wheel 112.

FIGS. 18 and 19 illustrate a further exemplary embodiment of a band drive device 115. Said band drive device also has only three rollers 111, 112, 113 which are responsible for imparting the band advancement, band retraction and band tensioning movements to the band by way of contact with the band, wherein the two rollers 111 and 112 can be driven by way of a motor, in particular by way of only one common motor. The relative arrangement of the axes of rotation of the three rollers 111, 112, 113 with respect to one another corresponds at least approximately to the arrangement of said axes of rotation in the exemplary embodiment of FIGS. 5 and 6.

The counterpart roller 113 is again designed to be pivotable, such that, in one pivoting position, it is provided for pressing the strapping band against the roller 111, and in another pivoting position, it is provided for pressing the strapping band against the tensioning roller 112. The pivoting mechanism, provided for this purpose, of the counterpart roller 113, and the drive of said pivoting mechanism, may in principle be of the same design as in the exemplary embodiment of FIGS. 1 to 13. As in the exemplary embodiment of FIGS. 5 and 6, the counterpart roller 113 is rotatably mounted on an eccentric 150, such that the counterpart roller 113 performs a non-circular-arc-shaped movement during a pivoting movement from one of the rollers 111, 112 to the respective other roller 111, 112. As shown in FIGS. 18 and 19, a clearance-generating device 180 is mounted on the eccentric 150 of the counterpart roller 113, wherein the clearance-generating device 180 is supported with a carrier 181 on the frame of the strapping apparatus 101. The bearing point 182 of the clearance-generating device on the eccentric 150 is itself arranged pivotably on the eccentric, and is in the form of a C-shaped or fork-shaped element 183 to thereby form a receptacle for one end of a piston 184. Said piston 184 is arranged in displaceable fashion in the carrier 181 of the clearance-generating device 180. In the illustration of FIGS. 18 and 19, the support point is situated immediately above the roller 111. The carrier 181 of the clearance-generating device is in this case likewise mounted in pivotable fashion.

In the exemplary embodiment shown, the clearance-generating device 180 is equipped with a clearance-generating element which is provided for performing a controlled movement by way of which the counterpart roller 113 is acted on in order for the counterpart roller 113, in its pivoted edition against the roller 111, to be moved such that a clearance is generated, or to be lifted slightly. The counterpart roller 113, in its pivoted position at the roller 111, should, even after the generation of a clearance, be able to be placed against the roller 111 again, for example likewise by way of the clearance-generating device. In the exemplary embodiment, the clearance-generating element is in the form of a solenoid 186 which is arranged and mounted on the clearance-generating device 180. The solenoid 186 can, by way of its piston 184, perform a linear stroke movement along the longitudinal axis 184 a of its piston 184. As shown in FIGS. 18 and 19, one end of the piston 184 is arranged in the recess, which is open toward the carrier 181, of the C-shaped or fork-shaped element 183. The end of the piston 184 and the recess of the C-shaped element may in this case be designed such that, during the clearance-generating movement, the end of the piston 184 in the C-shaped element can move relative thereto.

Here, the extended longitudinal axis 184 a of the piston 184 runs at least approximately through the articulation point of the C-shaped element 183. A stroke movement of the piston 184 in the direction of the counterpart roller 113 thus leads to a rotational movement of the eccentric about its axis of rotation. In the illustration of FIG. 18, the rotational movement takes place counterclockwise, as can be seen from a comparison of the two FIGS. 18 and 19. The rotational movement of the eccentric 150 in turn has the effect that the axis of rotation of the counterpart roller 113 is displaced in parallel and a gap, or an enlarged gap, is formed between the roller 111 and the counterpart roller 113. The width of the gap should in this case have a size greater than the thickness of the strapping band being processed in each case. As a solenoid, use may for example be made of the product GKb-32.06 from the company Isliker Magnete AG, CH-8450 Andelfingen.

On the piston 184 there may be arranged a mechanical spring element, in particular at least one compression spring 188. Said compression spring 188 is compressed, and thus braced in resiliently elastic fashion, during the movement of the counterpart roller 113 from the tensioning roller 112 into contact with the roller 111. The electrically actuable magnetic stroke-performing piston is deactivated, and thus has no action, in this phase. During the stroke movement, the compression spring 188 is at least partially relaxed and the spring force acts so as to assist the force imparted by the solenoid, by way of which force the piston 184 is moved so as to generate a clearance between the counterpart roller 113 and the roller 111. In other exemplary embodiments, in which the solenoid or some other restoring element alone provides a force high enough for the clearance-generating process.

During the production of the strap, it is the case—as already described—that, by way of the roller 111 and the counterpart roller 113 which bears against the former roller and clamps the band between the two rollers, the band is moved through the band guide channel 28 in a feed direction. When the strapping band reaches the region of the end of the band guide channel, as is illustrated by way of example in highly schematized form in FIG. 1, the band strikes a stop, or the fact that the end of the band guide channel has been reached may be detected in some other way, for example by way of a light barrier. In this way, a signal is generated, by way of which the control of the strapping apparatus stops the motor drive movement of the roller 111 and—at least substantially at the same time—triggers the stroke movement of the piston 184 of the solenoid. In other embodiments of the present disclosure, it is also conceivable for the stoppage of the drive movement of the roller 111 and the start of the clearance-generating process to have a time offset with respect to one another, that is to say for the stoppage of the drive movement to be performed before or after the start of the clearance-generating process.

As a result of the starting of the clearance-generating process, the piston 184 deploys in the direction of the C-shaped element 183 and, here, acts by way of its end on the C-shaped or fork-shaped element. Owing to its arrangement on the eccentric 150, the eccentric is rotated during the stroke movement of the piston. In the exemplary embodiment and in the illustration of FIG. 18, the rotational movement of the eccentric takes place through a rotational angle of less than 90° counterclockwise. The rotational movement takes place counter to the spring force of the pressure-exerting spring 190, which in this case is compressed and is likewise articulated on the eccentric 150. As a result of the rotational movement, a clearance is generated between the counterpart roller 113 and the roller 111, that is to say the counterpart roller 113 is lifted from the roller 111, and the spacing between the two rollers 111, 113 is enlarged such that a gap forms between the rollers, which gap is larger than the band thickness.

In the case of generic strapping apparatuses, the strapping band, which is shot at high speed through the band channel of the band guide 6, has the tendency, owing to the sudden and abrupt stoppage of the band, to form convolutions between the rollers 111, 112, 113 and the end of the strapping channel. In particular in the region of the rollers 111, 112, 113, such convolutions can lead to malfunctions. Owing to the embodiment according to the present disclosure, in which a clearance of the counterpart roller 113 is generated, the band can, in particular immediately after the stoppage of the advancement, move freely counter to the advancement direction in the direction of the band supply to the extent required for that part of the band which is possibly excess in relation to the length of the band channel, and which causes the formation of convolutions, to move back in the band guide channel. The controller of the strapping apparatus can then subsequently deactivate the solenoid again. As a result, the solenoid is rendered inactive, whereby the pressure-exerting spring 190 can move the eccentric 150 back again counter to the previous direction of rotation, and thus move the counterpart roller 113 into its position of contact with the band again, in which the band is clamped between the roller 111 and the counterpart roller 113. The subsequent band retraction and tensioning process can be performed in the same way as in the embodiments of the present disclosure as per FIGS. 1 to 13.

LIST OF REFERENCE DESIGNATIONS

-   1 Strapping apparatus -   2 Controller -   3 Supply device -   5 Strapping head -   6 Band guide -   8 Frame -   11 Roller -   11 a Circumferential surface -   12 Tensioning wheel -   12 a Circumferential surface of tensioning wheel -   13 Counterpart roller -   14 Motor -   14 a Mechanism device -   15 Band drive device -   16 Control component -   17 Band handling component -   18 Partial carrier -   19 Main carrier -   20 Band advancement device -   21 Band retraction device -   22 Tensioning device -   23 Axle -   27 Pivoting device -   28 Band guide channel -   28 a Channel section -   28 b Outer delimitation -   29 Interface -   30 Clamping lever -   31 Channel piece -   32 Band advancement direction -   33 Outer channel segment -   37 Ring -   38 Recess -   39 Knurling/toothing -   40 Groove -   43 O-ring -   44 O-ring -   45 Ring -   48 Band retraction direction -   50 Eccentric -   51 Shaft -   52 Carrier -   53 Receptacle -   54 Bearing point -   56 Parallelogram -   57 Long vertical lever -   58 Horizontal lever -   59 Short vertical lever -   60 Pivot bearing point -   61 Pivot bearing point -   64 Oblique surface -   65 Bearing point -   66 Carrier -   67 Rotary axle -   68 Rotary axle -   70 Spring element -   71 Articulation point -   72 Peg -   101 Strapping apparatus -   111 Roller -   112 Tensioning wheel -   112 a Circumferential surface -   112 b Part -   112 c Part -   113 Counterpart roller -   114 Screw -   115 Band drive device -   137 Ring -   140 Groove -   143 Ring section -   145 Ring -   150 Eccentric -   180 Clearance device -   181 Carrier -   182 Bearing point -   183 C-shaped element -   184 Piston -   184 a Axis -   186 Solenoid -   188 Compression spring -   190 Pressure-exerting spring -   B Width -   H Height 

The invention claimed is:
 1. A strapping device for strapping a packaged article with a strapping band, the strapping device comprising: a band guide; an advancement/retraction roller drivable to advance the strapping band through the band guide and afterwards to retract the strapping band from the band guide to cause the strapping band to be laid against the packaged article; a tensioning roller drivable to increase a band tension in the strapping band laid against the packaged article; a counterpart roller pivotable between a first position in which the counterpart roller is adjacent to the advancement/retraction roller and a second position in which the counterpart roller is adjacent to the tensioning roller; a clearance-generating device operably connected to the counterpart roller and configured to move the counterpart roller relative to the advancement/retraction roller; and a controller configured to, when the counterpart roller is adjacent to the advancement/retraction roller, control the clearance-generating device to move the counterpart roller to increase the spacing between the counterpart roller and the advancement/retraction roller; wherein the controller is configured to actuate the clearance generating device to move the counterpart roller to increase the spacing between the counterpart roller and the advancement/retraction roller after advancement of the band through the band guide and before retraction of the band from the band guide.
 2. The strapping device of claim 1, further comprising only one motor operably connected to: (1) the advancement/retraction roller and configured to drive the advancement/retraction roller in a first direction of rotation to advance the strapping band and a second different direction of rotation to retract the strapping band; and (2) the tensioning roller and configured to drive the tensioning roller.
 3. The strapping device of claim 2, wherein the only one motor is not configured to drive the counterpart roller.
 4. The strapping device of claim 1, wherein the increased spacing is greater than a thickness of the strapping band.
 5. The strapping device of claim 1, wherein the clearance-generating device comprises a piston movable between a first position and a second position, wherein the piston is operably connected to the counterpart roller and configured so movement of the piston from the first position to the second position causes the counterpart roller to move to increase the spacing between the counterpart roller and the advancement/retraction roller.
 6. The strapping device of claim 5, wherein the first position is a retracted position and the second position is an extended position.
 7. The strapping device of claim 6, wherein the clearance-generating device further comprises a biasing element configured to bias the piston to the extended position.
 8. The strapping device of claim 6, further comprises a biasing element configured to bias the piston to the retracted position.
 9. The strapping device of claim 6, wherein the clearance-generating device comprises a solenoid.
 10. The strapping device of claim 5, further comprising an eccentric on which the counterpart roller is rotatably mounted.
 11. The strapping device of claim 10, wherein the eccentric comprises a receptacle sized and shaped to receive a free end of the piston.
 12. The strapping device of claim 11, wherein movement of the piston from the first position to the second position causes the piston to act on the receptacle and cause the eccentric to rotate, thereby increasing the space between the counterpart roller and the advancement/retraction roller. 